Pump or motor



E. K, BENEDEK v ,Sept 2, 1947,

PUMP OR MOTOR Filed Feb. e, 1945 4 sheets-sheet 1 N n mm: E

A s Rmw wm. @D mK A Sept 2, 1947. 2,426,58

E. K. BENEDEK PUMP on MOTOR Filed Feb. e, 1945 4 sheets-snee; 2

P1 Z 69 I 60 E. K.KBENEDEK PUMP on Moron Filed Feb. 6, 1945 Sept. 2, 1947.

4 Sheets-Sheet 3 f' Vl. w, M

` wanton ELEK KBENEDEK @wwf @MS04/M35 Sept. 2, 1947 E'. K. BENEDEK PUMP OR MOTOR "Filed Feb,l 6, 1945 4 sheets-sheet 4 Patented Sept.` 2, 1947 UNITED I STATES PATENT OFFICE PUMP R MOTOR ElekI K. Benedek, Chicago, Ill.

Application February 6, 1945, Serial No. 576,408

(Cl. S- 161) 26 claims. l

This invention relates to pumps or motors and more 'particularly to hydraulic pumps of motors of the kind including a cylinder barrel rotatable about a xed pintle and in which pistons reciprocable in circumferentially spaced radial cylinders on the barrel are operated by thrusttransmitting means engageable with a reactance member or assembly eccentric to the pintle axis.

An object of the invention is to provide structural improvements-in a pump or motor of the class referred to by which the machine is made capable of operating with increased reliability and eiiiciency and at very high working pressures.

Another object ofthe invention is to provide a pump or motor having these desirable characteristics and which is of light, compact construction.

Another object of the invention is to provide a pump or motor of the character referred 'to in cluding new and improved means for lubricating a bearing interposed between the cylinder bar'- rel and the casing for journaling the cylinder barrel and anchoring it against axial shifting.

Another object of the invention is to provide an improved reactance member 4which can easily be assembled to provide perfect alignment of the component parts.

Another object is to provide such a reactance member or assembly in which new, simple, and effective means is employed for preventing .the unscrewing of bolts, or screws, which fasten the parts together.

Another object of the invention is to provide a pump or motor of the character stated in which the cylinder barrel may be driven or may drive through a detachable cap adapted to be removed endwise or vaxially through an lopening in the casing end Wall to permit inspection of internal parts.

A further object of the invention is to provide a new and improvedv arrangement of intercommunicating ducts, passages, grooves or the like for maintaining the fluid pressure acting on the pintle surface substantially in balance around the pintle so as to avoid deilection or straining of the pintle by unbalanced fluid pressure such as usually acts on different parts of pintles of pumps or motors of the kind in which the invention may be embodied.

Other objects of the invention will become apparent from a reading of the following detailed description, the appended claims, and the accompany drawings, in which:

Figure 1 is a longitudinal section of a hydraulic pump or motor embodying the invention,

the section being taken on the line I-I of Figure 2; 'i

Figure 2 is a transverse section on the line 2-2 of Figure 1;

Figure 3 is a longitudinal section of .a check l viewed from the left in Figure 6;

Figure 8 is a transverse -section of the'pintle on the line 8--3 of Figure 6;

Figure 9 is a transversesection of the pintle on either of the lines 9-9 in Figure 6, the pintle section being the same in the planes denoted by both of the lines 9 9;

Figure 10 isa section of the pintle on the line itimorrigure 6;

' Figure l1 is an end elevation of the pintle as viewed from the right of Figure 6;

Figure 12 is a view the same as Figure 9 but drawn on an enlarged scale;

Figure 13 is an elevation of a reactance end plate;

Figure 14 is a section 'on the line Ii-Ifi of Figure 13;

Figure 15 is a fragmentary elevation of a polygonal inner reactance ring as viewed when lool:n ing directly upony one of a plurality of iiat thrusttransmitting surfaces;

Figure 16 is an edge view of the structure shown in Figure l5; y

Figure 17 is a section on the line Il-I'I of Figure 16;

Figure 18 is a detail view showing' an outer `thrust-transniitting block; partly in section and The embodiment shown in the drawings com-- prises a pump casing generally designated A and including a cylindrical body portion I and a manifold cover plate .2 mounted at the open end of the body I and clamped and heldin assembled relation to the vbody I by bolts or other suitable means (not shown). The end lcover 2 supports one end of a pintle B which extends into the casing and is surrounded by a rotatable cylinder barrel'member C provided with two sets of circum-v Y ferentially spaced radial cylinders 3. Cylinder vports 4 communicating'with thecylinders 3 arev `adapted to cooperate in a known manner with ly towards the axis of the bore I9 and facing t0- wards the right hand end of the cylinder barrel C.

' The inner bearing race 28 is held in abutment with pintle discharge ports and intake ports 6. The

pintle discharge ports 5 communicate with discharge passages 1 extending longitudinally with `in the pintle to radial discharge passages 8 in nection I0. Similarly, the pintle intake ports 6 communicate with a large intake passage Il extending longitudinally through the pintle and. be-

ing connected to radial passages I2 which cornmunicate with a manifold intake chamber I3 adapted to communicate with outside piping through a connection I4.

Pistons I5 mounted for reclprocation in the cylinders 3 respectively are formed or equipped with tangential cross heads or thrust-transmitting connections I6 adapted to have rotary drive and thrust-transmitting connection with a reactance ring member or assembly D,'the construction of which will be explained later. For the present it is sumcient to state that the reactance ring assembly D is mounted for rotation about an axis eccentric to the common axis of the pintle and cylinder barrel.

In operation, the cylinder barrel C is rotated about the pintle B whereby the pistons I5 and the cross heads I6 impart rotary drive to the reactance ring assembly D and, due to the eccentricity ofthe assembly D, the pistons are reciprocated. The registration of the cylinder ports 4 with the pintle ports 5 and 6 is so timed with respect to `this shoulder by a shoulder 29 on a barrel end cap 30 detachably secured to the cylinder barrel C by screws or suitable fastenings,;.(not shown) and located with respect to the cylinder barrel by meansofapin3l.

The barrel end cap 30 is formed with a journal extension 32 which projects in axial align'- mentwith the pintle and extends through an opening 33 in the adjacent end of the casing. The wall ofthe opening 33 is larger in diameter than the barrel end cap 30 so as to permit the cap to be inserted into the casing axially with respect to the pintle in assembling, and to be removed from the casing for inspection of bearings or other internal parts.

Although the cylinder barrel C is mounted for rotation by bearings interposed between the barrel and the pintle, it is desirable also to provide bearings between a part of the cylinder barrel, for example the' end cap 30, and the casing. In the form shown, a ball bearing assembly interposed between the journal extension 32 and the casing body I includes an outer race 34 surrounding and fitting the journal 32, a set of balls 35,

and an inner race 36 tted within the wall of the casing opening 33. A snap ring 31 attached to the journal extension' 32 abuts the inner race 36 and holds it against a shoulder 38 on the end cap 30. The outer race 34 is held against axial movement by a ring nut closure 39 screwed into the end of the casing body I so as to press a snap ring 40 attached to the outerrace 34 into mutual engagement with a shoulder 4l!a formed in the casing body I.

the in-and-out travel of the pistons that iluid is drawn in to the cylinders during outward strokes of the pistons and is forced from the cylinders bore I8 in the cylinder barrel and preferably is formed of the same material, e. g., steel, as the cylinder barrel so as to provide for equal expansion and contraction in. response to temperature changes. A bore I9 in the sleeve I1 and counterboresf20 and 2l at the ends of the cylinder barrel C preferably are finished machined after the sleeve I1 has been fitted into the bore I8. The bore I9 in the sleeve I1 is of such diameter as to provide a close operating clearance space between the wall of the bore and the pintle B.

lThe cylinder barrel C is antifrictionally mounted on the pintle B for rotation about the pintle axis. At the left hand end of the cylinder barrel C, as viewed in Figure 1, the barrel is mounted by a roller bearing assembly including a set of rollers 22 directly engaging a pintle race section 23, and an outer race 24 press tted into the barrel counterbore 20. A snap ring 25 abutting the outer end face of the race 24 holds the opposite end face against a shoulder 201l atA the inner end of the counterbore 20.

At its right hand end the cylinder barrel C is mounted on the pintle by a roller bearing assembly including a set of rollers 26 directly engaging a reduced diameter pintle race section l21,'and an A,outer race 28 press fitted in the'counterbore 2I.

` or bushing I1 which is press fitted into a central I The journal extension 32 is hollow and is closed adjacent its inner end by a plug 4I. The outer end of the journal extension 32 is splined as at 42 to receive the splined inner end of a coupling 43, the outer end of which is splined as 'at 44 for engagement with an internally splined coupling part of a prime mover (not shown). A screw 45 anchored in the plug 4I extends through the coupling 43 and is provided with a nut 46 for preventing separation of the coupling 43, from the journal extension 32.

In operation, fluid is forced under high pressure from the cylinders 3,constituting a source of lubricant, through the cylinder ports 4 and thence out through the pintle discharge ports 5 and passages 1. Some of the high pressure iluid will be forced into the clearance space between the pintle B and the bore I9 and Will work its way along the pintle in both directions so as to lubricate thefantifriction bearings 22, 24 and 26, 28,. Slip fluid which hasworked toward the right past the bearing 26, 28 will collect in an inner lubricant chamber 41 defined by the free end of the pintle B and the wall provided by the end cap 30 and the plug 4I. In accordance with the invention means are provided for maintaining a supply Y of lubricating fluid in the chamber 41 and for delivering lubricant from this chamber directly to the bearing assembly 34, 35, 36. In the illustrative embodiment this is accomplished by providing the plug 4I with a, hollow portion or recess 48 communicating with an outer circumferential plug groove 49 by way of a plurality of radial passages 50, the barrel groove 49 being arranged to deliver lubricant through a lubricant passage 5I which discharges lubricant directly on the bearing assembly 34,35, 36.

lubricant chamber 41 and the outer lubricant chamber constituted by the plug recess 48 and vthrough the barrel-pintle clearance, the fluid under pressure in the chamber 41 is available for lubrication. The valve shown is of conventional construction and includes a passage 53 terminating ln a valve seat 54 adapted to be closed by a vthe `bolts 69 and the accommodating holes through the polygonal ring 59 so as to provide for 'flexibility and ease of assembling. This is permissible because theouter thrust transmitting surfaces 68 of the blocks 60 are maintained in perfect parallelism with the respectively associball valve 55 urged toward the seat by a springl 56 held in place by an apertured nut 51.

When the pump is running the pressure of the slip fluid contained in the inner chamber 41 will build up so as to open the valve 52, whereupon uid will ow into the outer chamber 49, 49 and thence through the passage I so as to lbe discharged directly upon the bearing assembly 34, 35, 36. The fluid 'contained in the outer chambers 48,'49 is whirled around rapidly so as to be under centrifugally created pressure resultingl ln its being delivered effectively upon the bearing assembly. When the pump stops the valve 52 closes so as to prevent back draining of the lubricant from the outer chamber 48. 49 thus assuring that the bearing assembly 34, 35, 36 will be lubricated effectively immediately upon starting of the pump.

The reactance assembly D comprises two simiated inner thrust transmitting surfaces 61 by mea-ns of thespacing flanges 66 on the blocks 60 which directly engage the inner thrust' transmitl ting surfaces-61. The outer thrust transmitting surfaces on the blocks 60 and the inner thrust transmitting surfaces 61 on the ring 59 respectively engage the outer and inner thrust'transmitting faces of the cross heads.

The reactance assembly D is journaled for ro tation about an axis eccentric to the common axis of the pintle B and cylinder barrel C. 1n th construction illustrated the assembly D is journaled in the casing by antifriction bearings interposed between the two ends of the assembly D and the casing body I. Each of these antifriction bearings includes an inner race 12 held on the associated end plate 53 by a snap ring 13, a set of balls 14, and an outer race l5 tted into the casing itself. The inner race 'l2 of the left hand bearing 12, 14, 15 abuts the heads 10 of the bolts or screws 69 so as toprevent them from working loose by unscrewing.

It will be seen that the bearing assembly 34, 35, 36 previously described anchors the cylinder barrel C against axial shifting. Consequently the manifold cover 2 and pintle B may be* removed as a unit endwise and to the left from the casing body l when it is desired to inspect the pintle.

inner reactance ring member 59, and a plurality f of individual outer thrust transmitting blocks' 60, all of which parts are held together securely to form a solid sub-assembly. The end plates 58 are formed with inner circumferential seats 6I surrounded and engaged respectively by axially spaced circumferential portions 62 on the inner ring 59. Openings 63 in the ring 59 freely accommodate the end portions of the pistons i5 which project beyond and clear of the cylinders 3.

The outer thrust transmission blocks 60 are formed with axially spaced arcuate portions 64 which are located radially within and which are engaged by outer circumferential seats S5 on the respective end plates 58. Radial spacing flanges 66 on the blocks 59 engage inner tangential thrust transmitting surfaces 51 on the polygonal ring 59 so that the blocks 69 are held between the flat surfaces 61 on the ring 59 and the outer circumferential seats 65 on the end plates 5B. This provides perfect parallel alignment between tangential outer thrust transmitting surfaces 68 on the blocks 69 and the respectively associated inner thrust transmitting surfaces 61 on the ring 59.

The end plates 58, the ring 59 and the blocks 60 are held in secure assembly by a plurality of circumferentially deployed bolts or screws 69 having threaded engagement with the right hand end plate 58 and having their heads 10 exposed at a radial surface at the left hand end plate as shown in Figure 1. The screws 69 draw the end plates 58 towards each other to clamp the polygonal ring 59 and the thrust blocks frictionally. A shroud ring 1| extends around the blocks 60 and overlaps the adjacent portions of the endl plates 58 so as to provide a continuous outer enclosing wall for the assembly D. v

Substantial clearance 69 isy provided between Removal of the Icover 2 and pintle Balso will permit inspection of the left hand pintle bearing 22-24. The pintle bearing 26, 28-may be exposed for inspection by removing the ring nut 39, bearing assembly 34, 35, 36 and cylinder barrel end cap 30 axially toward the right. Thus the pintle and the pintle bearings, `which are subjected to the hard service, may be inspected quite easily without any major disassembling of the pump,v

In order to remove the bearing assembly 26, 28, the ring nut 39 is removed, the snap ring 31 taken oil, and the entire rotatable assembly is removed from the casing endwise toward the left as viewed, in Figure 1, together with the pintle B` and end cover 2. The bearing 26, 28 is then radially accessible.

When the-pump is operating to deliver under high pressure, the cylinder and piston assemblies 3-l5 which communicate with the discharge ports 5 exert veryhigh fluid pressure on one side of the pintle B (thev top side as viewed in Figure 2) whereas the other side of the pintle (the bottom side as viewedin Figure 2) is under 'low or negative pressure. In Figures 6 to l2 the top and bottom sidesv of the pintle are shown divided by a median plane M-M which passes through bridge portions 16, 16 located on opposite sides of the pintle between the high pressure ports 5 and the low pressure ports 6. Heretofore the high pressure fluid acting .above the plane M--M has been an unbalanced positive pressure tending to deflect the cantilever pintle downwardly. Although, in theA pump shown in the drawings, the free end of the pintle is supported through the bearing assembly 2li- 28, the cylinder barrel and the bearing assembly 34, 35, 36, such an unbalanced Huid pressure could cause a small amount of pintle deflection which would increase the clearance between the pintle and the sleeve bore I9 on the high pressure side vof the plane M-M anddecrease 'the clearance on l the low pressure-side of cordance with the invention this tendency of the vv y the plane M-M. In acpintle to deflect so as to form unequal operating clearances on the high and low pressure sides,

and to subject the pintle to strain is eliminated or minimized by balancingor substantially equalizing the nuid pressure exerted on the pintle above and below the median plane M-M. Generally stated, this is accomplished by providing means for subjecting a surface portion of the pintle B on the bottom or low pressure side of the plane M-M to pressure of the order of the pressure in the high pressure passages 7. vPreferably also means is provided for subjecting a surface portion of the pintle B on the top or high r pressure side of the plane M-M to pressure of the order of the pressure in the low pressure passage Il. The pressure balancing is provided by leading high pressure uid to the clearance space between the pintle and the bore I9 below the y plane M-M, and by placing the low pressure ports 6 in communication with the clearance space above the plane M-M.

, high pressure iluid in the balancing grooves 'Il on the low pressure side of the pintle. The pressure uid in the grooves 1l will spread axially from both sides of the grooves so as to compensate for the low pressure of the iiuid in contact with the pintle immediately adjacent the pintley ports 6.

vto` and from said cylinders; pistons reciprocable in said cylinders respectively; thrust transmitting crossheads respectively on the ends of said pistons projecting clear of said cylinder barrel; and" a reactance assembly mounted to rotate about an axis eccentric to the cylinder barrel axis and being cooperable with'said crossheads for recipro- Y eating said pistons when said cylinder barrel and said reactance assembly rotate, said reactance assembly comprising two axially 'spaced end plates, an integralinner reactance ring formed with openings through which said piston projecting ends respectively extend and also being formed with tangential inner thrust-transmitting surfaces respectively engaging the inner faces of said crossheads, a plurality of individual outer thrust-transmitting blocks formed with tangential outer thrust-transmitting surfaces respectively engaging the outer faces of said crossheads, and means for drawing said end plates axially .towards each other to clamp said reactance ring and said thrust blocks between said enl plates and hold said reactance ring and s aid thrust blocks frictionally in circumferentially adjusted positions. 1

-3. In a pump or motor, a casing; a pintle mounted in the casing; a cylinder barrel rotatable relatively to said pintle; radial cylinders in said cylinder barrel; valve means for controlling now to and from said cylinders; pistons reciprocable in said cylinders respectively; thrust-transmitting crossheads respectively on the ends of said pistons ,projecting clear of said cylinder barrel; and a reactance assembly mounted to rotate about an axis eccentric to the cylinder barrel laxis and being cooperable with said crossheads for reciprocating said pistons when said cylinder barrel and On the top or high pressure side of the plane M-M the pintle is formed with two-balancing grooves 19 which are connected by balancing passages llextending through the pintle structure to the suction or lowl pressure passage II. The zone of low pressure uid thus created at and adjacent the grooves 'I9 tends to balance the high pressure acting on the pintle immediately adjacent the discharge ports 5. I have found that this uid balancing'of the pintle not only results in less wear on the pintle bearings but makes it possible to operate the pump with less clearance between the pintle and the cylinder barrel borel I 9 than heretofore has been advisable.

I claim:

1. In a pump or motor, s, casing; a pintle mounted at one'of its ends in the casing; a cylinder barrel .rotatable about said pintle and having means providing an end wall spaced from,

the opposite end of said pintle to provide a lubricant chamber for receiving slip iiuid discharged adapted to discharge beyond said wall; and a relief valve assembly removably mounted as a unit in said wall and being responsive to pressure for permitting uid to now from said chamber outwardly through said passage, but not reversely.

2.*In .a pump or motor, a casing; a pintle mounted in the casing; a cylinder barrel rotatable relatively to said pintle; radial cylinders in said cylinder barrel; valve means for controlling flow said reactance assembly rotate, said reactance assembly comprising two axially spaced endy plates each formed with inner and outer circumferential seats, an integral inner reactance ring axially spaced portions of which respectively surround and engage said inner circumferential seats and said ring being formed with openings through which said piston projecting ends respectively extend and also being formed with tangential inner thrust-transmitting surfaces respectively engaging the inner faces of said crossheads, a plurality of individual outerthrust-transmitting blocks engaging said reactance ring and having axially spaced portions respectively radially within and engaged by said outer circumferential seats, said-blocks being formed with tangential outer thrust-transmitting surfaces "respectively engaging the outer faces of said crossheads, and means for drawing said end plates axially towards each other to clamp said reactance ring and said thrust blocks between said end plates and hold said reactance ring and` said thrust blocks frictionally in circumferentially adjusted positions.

4. In a lpump or motor, a casing; a pintle mounted in the casing; a cylinder barrel rotatable relatively to said pintle; radial cylinders in ,said cylinder barrel; valve means for controlling flow to and from said cylinders; pistons reciprocable in said cylindersv respectively; thrustf heads for reciprocating said pistons when said cylinder barrel and said reactance assembly rotate, said reactance assembly comprising two axially spaced end plates, an integral inner reactance ring formed with openings through which said piston projecting ends respectively extend and yalso being formed with tangential inner thrust-transmitting surfaces respectively engaging the inner faces of said crossheads, a plurality of individual outer thrust-transmitting blocks formed with tangential outer thrust-transmitting surfaces respectively engaging the outer faces of said crossheads, and a plurality of circumferentially deployed clamping bolts for drawing said end plates axially towards each other to clamp said reactance ring and said thrust blocks between said'end plates and hold said reactance ring and said thrust blocks frictionally in circumferentially adjusted positions, said inner reactance ring being formed withl a plurality of holes through which said bolts extend with substantial radial clearance.

5. In a pump or motor, a casing; a pintle mounted in the casing; a cylinder barrel rotatable relatively to said pintle; radial cylinders in said spaced portions of which respectively surroundf, and engage said inner circumferential seats and said ring being formed with openings through which said piston projecting ends respectively extend and also being formed with tangential inner thrust-transmittingsurfaces respectively engaging the innerfaces of said crossheads, a plurality of individual outer thrust-transmitting blocks engaging said reactance ring and having' axially spaced portions respectively radially within and engaged by said outer circumferential seats, said blocks being formed with tangential outer thrust-transmitting surfaces respectively engaging the outer faces of said crossheads, and a plurality of circumferentially deployed clamping bolts for drawing said end plates 'axially towards each other to clamp said reactance ring'v and said thrust blocks between said end plates and hold said reactance ring andisaid thrust blocks frictionally in eircumferentially adjusted positions, said inner reactance ring being formed with a plurality of holes through which said bolts extend with substantial radial clearance.

6. In a pump or motor, a casing; a p intle mounted in the casing; a cylinder barrel rotatable relatively to said pintle; radial cylinders in said cylinder barrel; valve means for controlling flow to and from said cylinders; pistons reciprocable in said cylinders respectively; thrust transmitting crossheads respectively on the ends of said pistons projecting clear of said cylinder barrel; and a reactance assembly mounted to rotate about an axis eccentric to the cylinder barrel axis and being cooperable with said crossheads for reciprocating said pistons when said cylinder barrel and said reactance assembly rotate, said reactance assembly comprising two axially spaced end plates, an integral inner reactance ring formed with openings through which said piston projecting ends respectively extend and also besaid reactance ring and said thrust blocks frictionally in circumferentially adjusted positions.

7. In a pump or motor, a casing; a pintle mounted in the casing; a cylinder barrel rotatable relatively to said pintle; radial cylinders in said` cylinder barrel; valve means for controlling flow to and from said cylinders; pistons reciprocable in said cylinders respectively; thrust transmitting crossheads respectively on the ends of said istons projecting clear of said cylinder barrel; and a reactance assembly mounted to rotate about an axis eccentric to the cylinder barrel axis and being cooperable with said crossheads for reciproeating said pistons when said cylinder. barrel and said reactance assembly rotate, said reactance assembly comprising two axially spaced end' plates each formed with inner and outer circumferential seats, an integral inner reactance ring axially spaced portions of which respectively surround and engage said inner circumferential seats and said ring being formed with openings through which said piston projecting ends respectively extend and also being formed with tangential inner thrust transmitting surfaces respectively engaging the inner faces of said crossheads, a plurality of individual outer thrust transmitting blocks engaging said reactance ring ahd having axially spaced portions respectively radially within and engaged by said outer circumferential seats, said blocks being formed with tangential outer thrust transmitting surfaces respecl tively engaging the outer faces of said crossheads and being formed also with radial spacing means engaging said inner reactance ring for maintaining said outer thrust transmitting surfaces radially spaced from and parallel to the respective inner thrust transmitting surfaces, and means for drawing said end plates axially towards each other to clamp said reactance ring and said thrust blocks between said end plates and hold said reactance ring and said thrust blocks frictionally in circumferentially adjusted positions.

8. An annular reactance assembly for cooperation with the piston crossheads of a rotary cylinder barrel, radial cylinder and piston pump or motor, said assembly comprising two axially spaced end plates; an integral inner reactance ring formed-With openings through which the pistons are adapted to project and also being formed with tangential inner thrust-transmitting surfaces adapted respectively to engage the inner faces of said crossheads, a plurality of individual outer thrust transmitting blocks formed with tangential outer thrust-transmitting surfaces adapted respectively to engage the outer faces of said crossheads, and means for drawing said end plates axially towards each other to clamp said reactance f ring and l said thrust-transmitting block between said end plates and hold said reactance ring and said thrust-transmitting blocks frictionally. in circumferentiaily adjusted positions.

9. An annular reactance assembly for cooperation with the piston crossheads of a. rotary cylinder barrel, radial cylinder and'piston pump or -motor, said assembly comprising two axially spaced end plates; an integral inner reactance ring formed with openings through which thepistons are adapted to project and also being formed with tangential inner thrust-transmitting surfaces adapted respectively to engage the inner faces of said crossheads,'a plurality of individual outer thrust-transmitting blocks engaging said reactance ring and having axially spaced portions respectively radially within and engaged by said outer circumferential seats, said blocks being formed with tangential outer thrust-transmitting surfaces adapted respectively to engage the outer faces of said crossheads, and means for drawing said end plates axially towards -each other` to clamp said reactance ring and said thrust-transmitting blocks between said end plates and hold said reactance ring and said thrust-transmitting blocks frictionally in circumferentially adjusted positions.

10. An annular reactance assembly for coopera-- tion with the piston crossheads of a rotary cylinder barrel, radial cylinder and piston pump or motor, said assembly comprising two axially spaced end plates; an integral inner-reactance ring formed with openings through which the pistons are adapted to project and also being formed with tangential inner thrust-transmitting surfaces respectively adapted to engage the inner faces of said cross-heads, a plurality of individual outer thrust-transmitting blocks formed with tangential outer thrust-transmitting surfaces respectively adapted to engage the outer faces of said Vcrossheads and' being formed also with radial spacing means engaging said inner reactance ring for maintaining said outer thrusttransmitting surfaces radially spaced from and parallel to the respective inner thrust-transmitting surfaces, and means for drawing said end plates axially towards each other to clamp said reactance ring and said thrust-transmitting blocks between said end plates and hold said reactance ring and said thrust-transmitting blocks frictionally in circumferentially adjusted posi` means and comprising axially spaced members and bolts passingthroughr one of said members and being screwed to the other of said members, the bolt heads being/exposed at a radial surface of said one of said members; means mounting said reactance assembly to rotate in said casing eccentrically to said cylinder barrel including an antifriction bearing comprising roller elements and a race fitted to said reactance assembly; and means for holding said race in abutting engagement with said exposed bolt heads for preventing said bolts from accidentally unscrewing.

Y 12 the adjacent end portion of said cylinder barrel: an end cap detachably secured to said cylinder barrel e'nd portion and engaging said bearing for holding it against axial displacement from between said pintle projecting end and said barrel end portion; an opening through said casing aligned with said end cap and being larger than said end cap whereby the latter may be removed from within said casing to provide access to said bearing; a journal extending axially from said end cap and through said` casing opening; an antifriction bearing assembly in said opening and including an inner race surrounding and fitted to said journal and held against axial movementv thereon in either direction, and an outer race fitted within the wall of said casing opening; mu-

tually engaging means on the casing and the 13. In a rotary pump or motor, a pintle; a.

cylinder barrel mounted for rotation relatively v about the pintle axis and yformed with a bore v12. In a rotary pump or motor, a casing; a A

pintle mounted at one of its ends in one end of said casing and projecting toward the other end of said casing;l a cylinder barrel; means mounting saidvcylinder barrel for rotation about said pintle including a bearing interposed radially between the projecting end of said pintle and receiving said pintle with a close operating clearance between the pintle and the bore wall; radial cylinders in said barrel; high pressure port means in said pintle on one side of a median plane of j said pintle; low pressure port means in said pintle on the opposite side of said median plane; pintle bridge portions located in said median plane and separating said high pressure port means from said low pressure port means; cylinder ports opening inwardly from the respective cylinders to said bore and being cooperable with said high and low pressure port means for valving flow to and from said cylinders; pistons reciprocable respectively in said cylinders; means for reciprocating saidpistons in response to rotation ofl said oylinde barrel relatively to said pintle; a balancing pas age providing communication between said low pressure port means and said operating clearance space on said one side of said median plane; and another balancing passage providing communication between said high pressure port means and said operating clearance space on said opposite side of said median plane.

14. In a rotary pump or motor, afpintle; al

said pintle; low pressure port means in said pintle on the opposite side of said median plane; pintle bridge portions located in said median plane and separating said high pressure port means from said low pressure port means; cylinder ports opening inwardlyfrom the respective cylinders to said bore and being cooperable with said high and low pressure port means for valving ilow to and from said cylinders; pistons reciprocable respectively in said cylinders; means for reciprocating said pistonsin responsev to rotation of said cylinder barrel relatively to said pintle; a rst groove in the pintle surface between said bridge portions and on said one side of said median plane; a balancing passage providing communication between said first groove and said low pressure port means; a second groove in the pintle surface between said bridge portions and onv said opposite side of said median plane; and a bal- 13 ancing passage providing communication between said second groove and said high pressure port means.

15. In a rotary pump or motor, a pintle; a cylinder'barrel mounted for rotation relatively about the pintle axis and formed with a bore receiving said pintle with a close operating clearance between the pintle and the bore wall; radial cylinders in said barrel; high pressure port means in said pintle on one side of a median plane of said pintle; low pressure port means in said pintle on the opposite side of said median plane; pintle bridge portions located in said median plane and separating said high pressure port means from said low pressure port means; cylinder ports opening inwardly from the respective cylinders to said bore and being cooperable with said high and low pressure port means for valving flow to and from said cylinders; pistons reciprocable respectively in said cylinders; means for reciprocating said pistons in response to rotation of said `cylinder barrel relatively to said pintle; and means lfor subjecting a surface portion of said pintle on said one side of said median plane to pressure of the order f the pressure in thelow pressure port means, and for subjecting a surface portion of said pintle on said opposite side of said median plane to pressure of the order of the pressure in the high pressure port means.

16. In a rotary pump or motor, a pintle; a cylinder barrel mounted for rotation relatively about the pintle axis and formed with a bore receiving said pintle with a close operating clearance between the pintle and the bore wall;` radial cylinders in said barrel; high pressure port means in said pintle onione side of a median plane of said pintle; 10W pressure'port means in said pintle on the opposite side of said median plane; pintle bridge portions located in said median plane and separating said high pressure port means from said low pressure port means; cylinder ports opening inwardly from the respective cylinders to said bore and being cooperable with said high and low pressure port means for valving flow to and from said cylinders; a high pressure passage extending internally in said pintle and communif eating with said high pressure port means; a low pressure passage extending internally in said pintle and communicating with said low pressure port means; pistons reciprocable respectively in said cylinders; means for reciprocating said pistons in response to rotation of said cylinder barrel relatively to said pintle; a balancing passage extending through the pintle structure between said low pressure passage and said clearance space on said one side of said median plane; and another balancing passage extending through the pintle structure between said high pressure passage and said clearance space on said opposite side of said` median plane.

17. In a pump or motor, a casing; a pintle mounted at one of its ends in said casing; a cylinder barrel rotatable about said pintle; an end wall structure removably secured to said cylinder barrel and being spaced from the opposite end of the pintle and forming with said pintle opposite end a chamber for'receiving slip fluid discharged from the barrel-pintle clearance; through said end wall communicating at one end with said chamber and at its'other end being adapted to discharge beyond lsaid end wall structure; and a relief valve assembly removably screw-threaded as a unit into said end wall structure and being responsive to pressure of iluid in said chamber for permitting fluid to flow from a passage said chamber outwardly through said passage, but not reversely, for thus maintaining a supply of' fluid under predetermined pressure in said chamber.

18. In a pump or motor,' a casing; a, pintle mounted at one of its ends in said casing; a cylinder barrel rotatable aboutsaid pintle; an end wall removably secured to said cylinderfbarrel and being spaced from the opposite end of the pintle; a hollow journal extension on` said end cover having an internally splined outer end; a hollow plug inserted in the inner end portion of said journal extension for closing the end thereof adjacent said opposite end of the pintle; said pintle opposite end, said end wall and said plug providing a chamber; asource of uid under pressure communicating with said chamber; a passage communicating with said chamber and exten-ding through said plug; a relief valve assembly removably mounted as a unit in said plug and being responsive. to pressure for permitting fluid to flow from said chamber outwardly through said passage, but not reversely; an externally splined drive coupling tted in the outer end of said journal extension; and means for connecting said coupling to said plug for retaining the coupling in the journal extension.

19. In a rotary pump or motor, a casing; a

pintle mounted at one of its ends in one end of said casing and projecting toward the other end of the casing, said other end of the casing having an end wall and a mounting ange in a plane substantially perpendicular to the pintle axis, and sai-d end wall being formed with an opening; a cylinder barrel journalled to rotate about said pintle within said easing; journal means drivingly associated with said cylinder barrel and extending through said end wall opening; an antfriction bearing assembly in said end wall opening and including an outer race fitted within the wall of said openingl and an inner race on said journal means; a shoulder on said casing;` means on said outel` race engaging-said shoulder for limiting movement of said race axially toward said one end oi` said casing; and a retainer detachably secured in said end wall opening and bearing against said outer race for holding said outer race against movement toward the opposite end of said casing.

20. Ina rotary pump or motor, a casing; a pintle mounted at one of its ends in one end of said casing and projecting'toward the other end of the casing, said other end 0f the casing having an end wall and a mounting ange in a plane substantially perpendicular to the pintle axis, and said end wall being formed with an opening; a cylinder barrel journalled to rotate about said pintle within said casing; journal means drivingly associated with said cylinder barrel and extending through said end wall opening; an antifriction bearing assembly in said end wall opening and including an outer race fitted within the wall of said opening and an inner race on said journal means; a shoulder on said casing; a snap ring on said outer race engageable with said shoulder for limiting. movement of said race axially toward said one end of the casing; and a retainer ring screw-threaded into said end wall opening and bearing against said outer race for pressing said snap ring against said shoulder' to lock said outer race against movement in said casing.

21. In a rotary pump or motor, a casing: a pintle mounted at one oi its ends in one end of said casing and projecting toward `the other, end

a cylinder barrel journalled to rotate about said pintle within said casing; journal means drivvingly associated with said cylinder barrel Aandv extending through said end wall opening; an 'antifriction bearing assembly in said end wall opening and including an outer race fitted within the wall of said opening and an inner race on said journal means; a shoulder on said casing;

` means on said outer race engaging said shoulder for limiting movement of said race axially toward said one end of said casing; a seal surrounding said journal means; and a retainer ring detachably secured in said end Wall opening for holding said seal vin operative position, and bearing against said outer race for holding said outer race against movement toward the `opposite end of said casing.Y

22. In a pump or motor, a casing; a pintle mounted at one of its ends in said casing; a cylinder barrel rotatable about said pintle and having a bore; an end wall structure on said barrel and having a bell shaped section and being spaced axially from the other end of said pintle, said other end of said pintle constituting a fixed wall portion of a iiuid chamber and said end Wall structure constituting a rotary Wall portion of said chamber; a self-contained relief valve associated with one of said wall portions; and discharge passage means cooperable with said relief valve to relieve the pressure in said chamber to reduce the hydrostatic pressure on the other of said wall portions of said chamber.l

' one of said wall portions; and discharge passage 23. In a pump'or motor,- a casing; a pintle mounted at one of its ends in said casing; a cylinder barrel rotatable about said pintle and having a bore; a bearing journalling said cylinder barrel in said casing' and' restraining axial movement of said cylinder barrel; an end wall strucber and said end-wall structure constituting aj rotary wall portion of said chamber; a self-contained relief valve associated with one of said wall portions; and discharge passage means cooperable with said relief valve to relieve the pressure lin said chamber to thereby reduce the axial component of hydrostatic pressure on saidrotary wallfportion and reduce the axial load on said bearing.

24. In a pump ormotor, a casing; a pintle mounted at one of its ends in said casing and having ports; a cylinder barrel rotatable about said pintle and having a bore in which said pintle is received with close operating clearance; an end wall structure on said barrel and having a bell shaped section and being spaced axially from the other end of said pintle, said other end of said pintle constituting a xed Wall portion of afluid chamber and said end wall structure constituting a rotaryvwall portion of said chamber; a self-contained relief valve associated with means cooperable with said relief valve to relieve the pressure in said chamber to reduce the hydro static pressure on the other of said wall portions of said chamber, said relief valve being capable of maintaining suicient pressure in said cham'- ber to eiect flow of fluid from said chamber into said clearance to envelope said pintle and exert a radial pressure onl the pintle surface opposite to the port of the instantaneous working pressure.

25. In a pump or motor, a casing; a pintle mounted at one of its ends in said casing; a cylinder barrel rotatable about said pintle and having a bore; an end wall structure on .said barrel and having a bell 'shaped section and being ,spaced axially from the other end of said pintle,

associated with one of said wall portions; and` discharge passage means cooperable with said relief valve to relieve'the pressurev in said chamber to reduce the hydrostatic pressure en the other of said wall portions of said chamber, said relief valve constituting a load transformer between'said xed wall portion and said rotary wall portion, whereby part of the radial load on said fixed wall portion will be transformed into axial load on said rotary wall portion.

2.6. In a pump or motor, a casing; a pintle mounted at one of its ends in said casing; a cylinder barrel rotatable about said pintle and having a bore; an end wall structure on said barrel and having a bell shaped section and being spaced axially from the other end of said pintle, said other end of said pintle constituting a fixed wall portion of a Iiuid chamber and said end wall structureA constituting a rotary wall portion of said chamber; a self-contained relief rvalve associated with one of said wall portions; and discharge passage means cooperable with said relief valve to relieve the pressure in said chamber to reduce the hydrostatic pressure on the other of said wall portions of said chamber, said relief valve constituting a load transformer between said iixed'wallportion and said rotary wall portion, whereby part of the radial load on said fixed wall portion will be transformed into axial 0 load on said rotary Wall portion to thereby adjust the load on the respective bearings of said wall members.

ELEK K. BENEDEK.

Ernst Apr. 24, 1945 

